EP3129604A1 - Machine and method for operating the machine - Google Patents

Machine and method for operating the machine

Info

Publication number
EP3129604A1
EP3129604A1 EP15744517.2A EP15744517A EP3129604A1 EP 3129604 A1 EP3129604 A1 EP 3129604A1 EP 15744517 A EP15744517 A EP 15744517A EP 3129604 A1 EP3129604 A1 EP 3129604A1
Authority
EP
European Patent Office
Prior art keywords
shaft
bearing
face
partition plate
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15744517.2A
Other languages
German (de)
French (fr)
Other versions
EP3129604B1 (en
Inventor
Joachim Krützfeldt
Oliver Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP3129604A1 publication Critical patent/EP3129604A1/en
Application granted granted Critical
Publication of EP3129604B1 publication Critical patent/EP3129604B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
    • F01D11/06—Control thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F01D11/04—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type using sealing fluid, e.g. steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/166—Sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F01D25/186—Sealing means for sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/06—Arrangements of bearings; Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F16J15/4476—Labyrinth packings with radial path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/28—Arrangement of seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F04D29/104—Shaft sealings especially adapted for elastic fluid pumps the sealing fluid being other than the working fluid or being the working fluid treated

Definitions

  • the invention relates to a machine with a shaft and egg ⁇ nem warehouse and a method for operating the machine.
  • a machine such as a turbomachine, having a shaft and an oil lubricated bearing may be provided with a seal gas seal to prevent the oil from leaking out of the bearing.
  • the seal gas seal may have a barrier chamber between a radially extending rotating shaft wall and the stationary bearing housing.
  • Bearing housing is low, so that the oil can escape from the bearing housing.
  • the leakage of the oil is particularly critical when it occurs at the turbine outlet of a gas turbine, because here the oil can come into contact with hot parts of the gas turbine.
  • the oil may coke or burn through contact, thereby jeopardizing the safe operation of the machine.
  • Conventionally, the problem is solved in which the sealing gas seal is acted upon by the barrier fluid under high pressure, which is disadvantageous for the efficiency of Gastur ⁇ bine.
  • a bearing arrangement is known from US 2012/201761 AI, in which an overpressure can be generated in a gap which is shielded in each case via a labyrinth seal on the one hand to a hydraulic bearing and on the other hand to a room with atmospheric pressure. Which he- Generation of the overpressure takes place with the aid of a fluid line, which opens into the intermediate space and with which a corresponding fluid can be supplied.
  • the gap can be further subdivided by a shield to the subspace with the local pressure increase as close to the end of the
  • the object of the invention is to provide a machine with a shaft and a bearing and a method for operating the machine, wherein a good sealing effect against the bearing is achieved.
  • the machine according to the invention has a shaft which has a foot , so that a first shaft section with a first diameter, a second shaft section with a second diameter, which is shorter than the first diameter, and a radially extending and rotatable Wel ⁇ lenstirnsynthesis are formed, a housing and a bearing, which supports the shaft at its second shaft portion on the housing and is lubricated with a lubricating fluid, wherein the shaft end face a radially extending and stationary bearing face facing, whereby one with a barrier fluid, by means of a Leakage of the lubricating fluid from the bearing can be prevented, beaufschlag ⁇ Baren barrier chamber is formed, which is bounded axially from the shaft end face and the bearing face and radially inward from the second shaft section released from the bearing, characterized in that the barrier chamber via a passage with the environment Blindfolded nden and that in the lock chamber, a radially extending and fixed partition plate is arranged, so that an aerodynamic shield
  • Shaft end face and the partition plate is axially bounded by a ro ⁇ -tendering wall, namely from the bearing end face, so that a vortex can form in this area.
  • this vortex does not affect the area between the separating plate and the bearing end face.
  • the barrier fluid in the area between the partition plate and the bearing face has substantially the pressure applied to the barrier chamber and is exposed only to wall friction losses.
  • the pressure of the barrier fluid at the bearing end side is high, whereby a good sealing effect against the bearing can be achieved.
  • the partition plate is such a simple con ⁇ structural measure that existing machines can be retrofitted with the partition plate.
  • a radial gap is formed between the radially inner longitudinal end of the partition plate and the shaft. This advantageously prevents grinding of the partition plate on the shaft.
  • the radial gap preferably has an extent in the radial direction of 0.1 mm to
  • the upper limit of 10 mm advantageously ensures that no vortex is formed in the region between the separating plate and the bearing end side.
  • ⁇ provides cleansege that can not get so much barrier fluid via the radial gap in the area between the shaft and the face of the partition plate that the pressure on the bearing front side drops significantly.
  • the partition plate is arranged parallel to the Wel ⁇ lenstirn preparation and the bearing end face. Since ⁇ comparable through to bottlenecks for the flow of barrier fluid to be avoided. The bottlenecks can disadvantageously lead to the formation of vertebrae.
  • the partition plate preferably has ei ⁇ NEN distance from the shaft end surface of from 0.25 to 0.75 * d * d, more preferably from 0.5 to 0.75 * d * d, particularly preferably 0.5 * d , is, where d is the distance between the Wel ⁇ lenstirn fabrication and the bearing end face.
  • the partition plate is arranged closer to the bearing end side than to the shaft end face in order to minimize the shear forces in the area between the rotating shaft end face and the partition plate.
  • the partition plate preferably extends radially outwards substantially to at least the radially outer end of the shaft end face.
  • the partition plate is arranged in a circular ring around the shaft.
  • the partition plate is preferably fixed by means attached to the bearing end face and on the partition plate spacers. This makes it possible to install the separator plate together with the bearing in the machine or remove it from the machine.
  • the bearing represents a wearing part of the machine and retrofitting the machine with the separating plate can thus be carried out particularly easily during a routine replacement of the bearing.
  • the machine is a turbomachine, in particular a gas turbine.
  • the barrier chamber is disposed with the partition plate at the turbine outlet of the gas turbine. It is above ⁇ geous to provide the separation plate here because leakage of the lubricating fluid at the turbine outlet of the gas turbine special ⁇ is the critical since it occurred there in contact with hot exhaust gases and hot parts of the gas turbine and can burn it.
  • the method according to the invention for operating a machine comprises the steps of: rotating the shaft; Inflicting the barrier chamber with ambient air under atmospheric conditions as the barrier fluid, whereby leakage of the lubricating fluid from the bearing is prevented in the barrier chamber.
  • ambient air is used, in particular from a
  • Figure 2 is a detail view of the longitudinal section of Figure 1 and
  • Figure 3 shows the flow conditions in a barrier chamber of
  • 1 has an Ma ⁇ machine on a shaft 2 which is rotier ⁇ about a shaft axis 8 bar. Furthermore, the shaft 2 has a step 3, where ⁇ through the shaft 2 in the axial direction, a first Wellenab- section 9 having a first radius 11 and a second Wel ⁇ lenabrough 10 having a second radius 12. The second radius 12 is shorter than the first radius 11.
  • the shaft 2 has a rotatable shaft end face 6, which is arranged in the interface between the first shaft portion 10 and second shaft portion 11 and radially between the first Radius 11 and the second radius 12 extends.
  • the shaft end face 6 is there ⁇ by annular.
  • the machine 1 further comprises a fixed housing 5 and a bearing 4, which supports the shaft 2 at its second shaft portion 10 on the housing 5.
  • the bearing 4 is lubricated with a lubricating fluid, in particular oil, and is in particular a slide bearing.
  • the bearing 4 has a fixed bearing end face 7, which is arranged parallel to the shaft end face 6 and the shaft end face 6 facing. Rad ⁇ al outside the bearing end face 7, a fixed housing end face 30 is arranged, which is also arranged facing the shaft end face 6.
  • the machine 1 has a blocking chamber 13, which is acted upon by a blocking fluid during operation of the machine 1 in order to prevent leakage of the lubricating fluid from the bearing 4 into the blocking chamber 13.
  • the locking chamber 13 is axially bounded by the shaft end face 6 and the bearing end side 7. Radially inside the locking chamber 13 is bounded by the radial outside of the shaft end face 6 to the bearing ⁇ end face 7 extending portion of the second Wellenab- section 10th
  • the bearing 4 has a bearing seal 14 for sealing the bearing 4 to the locking chamber 13 out.
  • the bearing seal 14 is arranged on the radial outer side of the shaft 2 in the region of the second shaft section 10 and in the region of the bearing end face 7 on ⁇ .
  • Seal 14 is higher than the pressure of the lubricating fluid at this ⁇ sem end.
  • the partition plate 15 In the barrier chamber 13 is a fixed and radially extending partition plate 15 is introduced.
  • the partition plate 15 may be a sheet, for example.
  • the partition plate 15 is arranged with its long side parallel to the shaft end face 6 and the bearing end face 7 and formed from annular ⁇ .
  • a rotor-stator chamber 27 extending from the shaft end face 6 to the partition plate 15 and a stator-stator chamber 28 are formed extending from the partition plate 15 to the bearing end face 7 extends.
  • the rotor-stator chamber 27 and the stator-stator chamber 28 are arranged side by side in the axial direction.
  • a radial gap 16 is formed, which has an extension of 0.1 mm to 10 mm in the radial direction.
  • the partition plate 15 has a distance from the shaft end face 6, which is from 0.25 * d to 0.75 * d, where d is the distance between the shaft end surface ⁇ 6 and the bearing end face 7. Radially outward ⁇ SEN, the partition plate 15 extends in accordance with Figures 1 to 3 substantially to the first radius 11. However, it is conceivable to also continue the separator plate 15 radially outward from.
  • the seal chamber 13 has a first recess 25 which is inserted into the shaft 2 and radially outwardly adjoining the ers ⁇ th radius. 11 Through the first recess 25 a recess end face 29 is formed, which is arranged facing the bearing ⁇ end face 7.
  • the locking chamber 15 also has a second recess 26 which extends radially outward.
  • the barrier fluid at atmospheric pressure can pass from the environment 23 of the machine 1 into the blocking chamber 13 via a passage through which it is possible to flow.
  • the passage comprises an Au walkedspalt 22, a channel 24 and the second recess 26 so ⁇ as not further illustrated channels, whereby the Sperrkam ⁇ mer 13 is in flow communication with the environment.
  • a turbine gap 20 extends from the barrier chamber 13 to a turbine interior.
  • the turbine gap 20 has a turbine seal 21. So that no exhaust gas from the turbine interior via the turbine gap 20 can get into the barrier chamber 13, it is necessary that the pressure of the sealing gas in the barrier chamber 13 is higher than the pressure of the exhaust gas.
  • the machine 1 has a plurality of spacers 17, which are respectively attached to the bearing end face 7 and to the partition plate 15 to fix the partition plate 17. Je ⁇ of the spacer 17 is performed by a respective hole in the partition plate 15 and has a spacer head, with the axial displacement of the partition plate 15 is limited in the direction of the shaft end face 6.
  • Each spacer 17 is enveloped by a sleeve 19, with which the axial displacement of the partition plate 15 is limited in the direction of the bearing end face 7.
  • stator-stator chamber 28 ie the area be- see the partition plate 15 and the bearing face 7, wirbelok in ⁇ We sentlichen.
  • stator-stator chamber 28 small vortices can be formed in corners or at edges, but these small vortices can not determine the pressure in the stator-stator chamber 27.
  • the pressure at the bearing end face 7 is higher than would be the case for a barrier chamber without partition plate. CFD calculations for some selected cases have shown that the pressure at the bearing end face 7 at the radially inner lie ⁇ ing end of the barrier chamber 13 by 2 mbar to 3 mbar higher than it would be the case for the barrier chamber without partition plate.
  • Locking chamber 13 by 1.5 mbar to 2.5 mbar higher than it would be the case for the barrier chamber without partition plate. It is in the barrier chamber 13 and at the radially outwardly of the first radius 11 arranged recess end face 29, the barrier fluid conveyed radially outward.
  • the partition plate 15 according to FIGS. 1 to 3 extends only substantially up to the first radius 11, the area radially outside the radius 11 is not critical because here the distance between the recess end face 29 and the bearing front side 7 and / or the housing end 30 is suffi ⁇ ciently large that no radial pressure gradient ausbil ⁇ can.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Rolling Contact Bearings (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

The invention relates to a machine comprising: a shaft (2) having a stage (3) such that a first shaft section (9) having a first diameter (11), a second shaft section (10) having a second diameter (12) that is shorter than the first diameter (11), and a radially extending and rotatable shaft end surface (6) are formed; a housing (5); and a bearing (4) which supports the shaft (2) on the housing (5) by its second shaft section (10), and which is lubricated by a lubrication fluid, wherein the shaft end surface (6) is facing a radially extending and stationary bearing end side (7), whereby a sealing chamber (13) is formed that can be applied with a sealing fluid, by means of which sealing fluid the lubrication fluid can be prevented from leaving the bearing (4), and which sealing chamber is axially limited by the shaft end surface (6) and the bearing end side (7), and radially inwardly limited by the second shaft section (10) released from the bearing (4), characterised in that a radially extending and stationary separator plate (15) is introduced into the sealing chamber (13), such that an aerodynamic shielding of the bearing end side (7) from the shaft end surface (6) is achieved, whereby, when the shaft (2) is rotating, the region between the separator plate (15) and the bearing end side (7) is substantially non-rotational.

Description

Beschreibung description
Maschine und Verfahren zum Betreiben der Maschine Machine and method for operating the machine
Die Erfindung betrifft eine Maschine mit einer Welle und ei¬ nem Lager sowie ein Verfahren zum Betreiben der Maschine. The invention relates to a machine with a shaft and egg ¬ nem warehouse and a method for operating the machine.
Eine Maschine, wie beispielsweise eine Strömungsmaschine, mit einer Welle und einem ölgeschmierten Lager kann mit einer Sperrgasdichtung versehen werden, um ein Austreten des Öls aus dem Lager zu unterbinden. Die Sperrgasdichtung kann eine Sperrkammer zwischen einer sich radial erstreckenden rotierenden Wellenwand und dem feststehenden Lagergehäuse aufwei- sen. Im Betrieb der Maschine, wenn die Welle rotiert und die Sperrgasdichtung mit einem Sperrfluid beaufschlagt ist, wird das Sperrfluid in der Sperrkammer über Reibung an der Wellenwand in Rotation versetzt. Im rotierenden Sperrfluid bildet sich durch die Wirkung der Zentrifugalkräfte ein Druckabfall nach radial innen aus, wodurch nachteilig der Druck an demA machine, such as a turbomachine, having a shaft and an oil lubricated bearing may be provided with a seal gas seal to prevent the oil from leaking out of the bearing. The seal gas seal may have a barrier chamber between a radially extending rotating shaft wall and the stationary bearing housing. During operation of the machine, when the shaft is rotating and the barrier gas seal is exposed to a barrier fluid, the barrier fluid in the barrier chamber is caused to rotate by friction on the shaft wall. In the rotating barrier fluid is formed by the action of centrifugal forces a pressure drop radially inward, thereby adversely affecting the pressure on the
Lagergehäuse gering ist, so dass das Öl aus dem Lagergehäuse austreten kann. Bearing housing is low, so that the oil can escape from the bearing housing.
Das Austreten des Öls ist besonders kritisch, wenn dies am Turbinenaustritt einer Gasturbine auftritt, weil hier das Öl in Kontakt mit heißen Teilen der Gasturbine treten kann. Das Öl kann durch den Kontakt verkoken oder verbrennen und dadurch den sicheren Betrieb der Betrieb der Maschine gefährden. Herkömmlich wird das Problem gelöst, in dem die Sperr- gasdichtung mit dem Sperrfluid unter hohem Druck beaufschlagt wird, was jedoch nachteilig für den Wirkungsgrad der Gastur¬ bine ist. The leakage of the oil is particularly critical when it occurs at the turbine outlet of a gas turbine, because here the oil can come into contact with hot parts of the gas turbine. The oil may coke or burn through contact, thereby jeopardizing the safe operation of the machine. Conventionally, the problem is solved in which the sealing gas seal is acted upon by the barrier fluid under high pressure, which is disadvantageous for the efficiency of Gastur ¬ bine.
Weiter ist aus der US 2012/201661 AI eine Lageranordnung be- kannt, bei der in einem Zwischenraum, welcher jeweils über eine Labyrinthdichtung einerseits zu einem hydraulischen Lager und andererseits zu einem Raum mit atmosphärischen Druck abgeschirmt ist, ein Überdruck erzeugt werden kann. Die Er- zeugung des Überdrucks erfolgt mit Hilfe eine Fluidleitung, die im Zwischenraum mündet und mit der ein entsprechenden Fluid zuführbar ist. Der Zwischenraum kann dabei durch eine Abschirmung weiter unterteilt werden, um den Teilraum mit der lokalen Druckerhöhung möglichst nahe am Ende der Furthermore, a bearing arrangement is known from US 2012/201661 AI, in which an overpressure can be generated in a gap which is shielded in each case via a labyrinth seal on the one hand to a hydraulic bearing and on the other hand to a room with atmospheric pressure. Which he- Generation of the overpressure takes place with the aid of a fluid line, which opens into the intermediate space and with which a corresponding fluid can be supplied. The gap can be further subdivided by a shield to the subspace with the local pressure increase as close to the end of the
Labyrinthdichtung anzusiedeln. Nachteilig ist jedoch hierbei, dass ein Überdruck zur Erzeugung einer zuverlässigen Abdichtung erforderlich ist.  To settle labyrinth seal. The disadvantage here, however, that an overpressure to produce a reliable seal is required.
Aufgabe der Erfindung ist es, eine Maschine mit einer Welle und einem Lager sowie ein Verfahren zum Betreiben der Maschine zu schaffen, wobei eine gute Dichtwirkung gegenüber dem Lager erzielt wird. The object of the invention is to provide a machine with a shaft and a bearing and a method for operating the machine, wherein a good sealing effect against the bearing is achieved.
Die erfindungsgemäße Maschine weist eine Welle, die eine Stu¬ fe aufweist, so dass ein erster Wellenabschnitt mit einem ersten Durchmesser, ein zweiter Wellenabschnitt mit einem zweiten Durchmesser, der kürzer als der erste Durchmesser ist, und eine sich radial erstreckende sowie rotierbare Wel¬ lenstirnfläche ausgebildet sind, ein Gehäuse und ein Lager auf, das die Welle an ihrem zweiten Wellenabschnitt an dem Gehäuse abstützt und mit einem Schmierfluid geschmiert ist, wobei die Wellenstirnfläche einer sich radial erstreckenden sowie feststehenden Lagerstirnseite zugewandt ist, wodurch eine mit einem Sperrfluid, mittels dem ein Austreten des Schmierfluids aus dem Lager unterbindbar ist, beaufschlag¬ baren Sperrkammer ausgebildet ist, die axial von der Wellenstirnfläche und der Lagerstirnseite sowie radial innen von dem von dem Lager freigelassenen zweiten Wellenabschnitt begrenzt ist, dadurch gekennzeichnet, dass die Sperrkammer über eine Passage mit der Umgebung verbunden ist und dass in der Sperrkammer eine sich radial erstreckende und feststehende Trennplatte angeordnet ist, so dass eine aerodynamische Ab- schirmung der Lagerstirnseite von der Wellenstirnfläche er¬ folgt, wodurch der Bereich zwischen der Trennplatte und der Lagerstirnseite beim Rotieren der Welle im Wesentlichen wirbelfrei, d.h. drallfrei ist. Der Bereich zwischen der Trennplatte und der Lagerstirnseite ist axial von keinen rotierenden Wänden begrenzt, so dass sich in diesem Bereich auch kein die Druckverhältnisse be- stimmender Wirbel ausbilden kann. Der Bereich zwischen derThe machine according to the invention has a shaft which has a foot , so that a first shaft section with a first diameter, a second shaft section with a second diameter, which is shorter than the first diameter, and a radially extending and rotatable Wel ¬ lenstirnfläche are formed, a housing and a bearing, which supports the shaft at its second shaft portion on the housing and is lubricated with a lubricating fluid, wherein the shaft end face a radially extending and stationary bearing face facing, whereby one with a barrier fluid, by means of a Leakage of the lubricating fluid from the bearing can be prevented, beaufschlag ¬ Baren barrier chamber is formed, which is bounded axially from the shaft end face and the bearing face and radially inward from the second shaft section released from the bearing, characterized in that the barrier chamber via a passage with the environment Blindfolded nden and that in the lock chamber, a radially extending and fixed partition plate is arranged, so that an aerodynamic shielding of the bearing end side of the shaft end face he follows ¬ , whereby the area between the partition plate and the bearing face during rotation of the shaft substantially eddy-free, that is, twist-free. The area between the partition plate and the bearing end face is axially bounded by no rotating walls, so that in this area also no pressure conditions can be determined. The area between the
Wellenstirnfläche und der Trennplatte ist axial von einer ro¬ tierenden Wand begrenzt, nämlich von der Lagerstirnseite, so dass sich ein Wirbel in diesem Bereich ausbilden kann. Dieser Wirbel wirkt sich jedoch aufgrund der abschirmenden Wirkung der Trennplatte nicht auf den Bereich zwischen der Trennplat¬ te und der Lagerstirnseite aus. Damit hat das Sperrfluid in dem Bereich zwischen der Trennplatte und der Lagerstirnseite im Wesentlichen den Druck, mit dem die Sperrkammer beaufschlagt ist, und ist nur Wandreibungsverlusten ausgesetzt. Damit ist der Druck des Sperrfluids an der Lagerstirnseite hoch, wodurch eine gute Dichtwirkung gegenüber dem Lager erzielbar ist. Die Trennplatte stellt eine derart einfache kon¬ struktive Maßnahme dar, dass bestehende Maschinen auch mit der Trennplatte nachgerüstet werden können. Shaft end face and the partition plate is axially bounded by a ro ¬ -tendering wall, namely from the bearing end face, so that a vortex can form in this area. However, due to the shielding effect of the separating plate, this vortex does not affect the area between the separating plate and the bearing end face. Thus, the barrier fluid in the area between the partition plate and the bearing face has substantially the pressure applied to the barrier chamber and is exposed only to wall friction losses. Thus, the pressure of the barrier fluid at the bearing end side is high, whereby a good sealing effect against the bearing can be achieved. The partition plate is such a simple con ¬ structural measure that existing machines can be retrofitted with the partition plate.
Es ist bevorzugt, dass zwischen dem radial innen liegenden Längsende der Trennplatte und der Welle ein Radialspalt aus¬ gebildet ist. Dadurch wird vorteilhaft ein Anschleifen der Trennplatte an der Welle unterbunden. Der Radialspalt hat be- vorzugt eine Erstreckung in Radialrichtung von 0,1 mm bisIt is preferred that a radial gap is formed between the radially inner longitudinal end of the partition plate and the shaft. This advantageously prevents grinding of the partition plate on the shaft. The radial gap preferably has an extent in the radial direction of 0.1 mm to
10 mm. Durch die Untergrenze von 0,1 mm kann vorteilhaft das Anschleifen unterbunden werden. Durch die Obergrenze von 10 mm wird vorteilhaft sichergestellt, dass sich kein Wirbel in dem Bereich zwischen der Trennplatte und der Lagerstirn- seite ausbildet. Durch die Obergrenze ist auch sicherge¬ stellt, dass nicht derart viel Sperrfluid via den Radialspalt in den Bereich zwischen der Wellenstirnfläche und der der Trennplatte gelangen kann, dass der Druck an der Lagerstirnseite wesentlich absinkt. 10 mm. Due to the lower limit of 0.1 mm can advantageously be prevented from grinding. The upper limit of 10 mm advantageously ensures that no vortex is formed in the region between the separating plate and the bearing end side. By the upper limit is ¬ provides sicherge that can not get so much barrier fluid via the radial gap in the area between the shaft and the face of the partition plate that the pressure on the bearing front side drops significantly.
Es ist bevorzugt, dass die Trennplatte parallel zu der Wel¬ lenstirnfläche und der Lagerstirnseite angeordnet ist. Da¬ durch können Engstellen für die Strömung des Sperrfluids ver- mieden werden. Die Engstellen können nachteilig zu der Ausbildung von Wirbeln führen. Die Trennplatte hat bevorzugt ei¬ nen Abstand von der Wellenstirnfläche, der von 0,25*d bis 0,75*d, weiter bevorzugt von 0,5*d bis 0,75*d, besonders be- vorzugt 0,5*d, beträgt, wobei d der Abstand zwischen der Wel¬ lenstirnfläche und der Lagerstirnseite ist. Durch den Min¬ destabstand der Trennplatte von der Lagerstirnseite ist vor¬ teilhaft sichergestellt, dass das Sperrfluid durch Reibung nicht derart aufgewärmt wird, dass es das Lager angreifen kann. Durch den Mindestabstand der Trennplatte von der Wel¬ lenstirnfläche ist ebenfalls vorteilhaft sichergestellt, dass sich das Sperrfluid nicht wesentlich durch Reibung aufheizt. Die Trennplatte ist eher näher zu der Lagerstirnseite als zu der Wellenstirnfläche angeordnet, um die Scherkräfte im Be- reich zwischen der rotierenden Wellenstirnfläche und der Trennplatte gering zu halten. It is preferred that the partition plate is arranged parallel to the Wel ¬ lenstirnfläche and the bearing end face. Since ¬ comparable through to bottlenecks for the flow of barrier fluid to be avoided. The bottlenecks can disadvantageously lead to the formation of vertebrae. The partition plate preferably has ei ¬ NEN distance from the shaft end surface of from 0.25 to 0.75 * d * d, more preferably from 0.5 to 0.75 * d * d, particularly preferably 0.5 * d , is, where d is the distance between the Wel ¬ lenstirnfläche and the bearing end face. By Min ¬ the partition plate from the bearing end face least distance is ensured before ¬ geous that the barrier fluid is not heated by friction so that it can engage the bearing. Due to the minimum distance of the partition plate from the Wel ¬ lenstirnfläche is also advantageously ensured that the barrier fluid does not heat up significantly by friction. The partition plate is arranged closer to the bearing end side than to the shaft end face in order to minimize the shear forces in the area between the rotating shaft end face and the partition plate.
Die Trennplatte erstreckt sich bevorzugt nach radial außen im Wesentlichen bis mindestens zu dem radial außen liegenden En- de der Wellenstirnfläche. Damit ist vorteilhaft eine derar¬ tige Abschirmung der Lagerstirnseite von der Wellenstirnflä¬ che erreicht, dass der Bereich zwischen der Trennplatte und der Lagerstirnseite beim Rotieren der Welle im Wesentlichen wirbelfrei ist. Es ist bevorzugt, dass die Trennplatte kreis- ringförmig um die Welle herum angeordnet ist. Indem die The partition plate preferably extends radially outwards substantially to at least the radially outer end of the shaft end face. Thus is advantageously a Derar ¬ term shielding the bearing end face of the Wellenstirnflä ¬ che achieved, that the area between the partition plate and the bearing end face during rotation of the shaft is substantially irrotational. It is preferred that the partition plate is arranged in a circular ring around the shaft. By the
Trennplatte unterbrechungsfrei und kreisringförmig in Um- fangsrichtung um die Welle herum angeordnet ist, können sich auch keine lokal begrenzten Wirbel zwischen der Trennplatte und der Lagerstirnseite ausbilden.  Separation plate without interruption and annularly arranged in the circumferential direction around the shaft around, no localized vortex between the partition plate and the bearing end face can form.
Die Trennplatte ist bevorzugt mittels an der Lagerstirnseite und an der Trennplatte angebrachten Abstandshaltern befestigt. Dadurch ist es möglich, die Trennplatte zusammen mit dem Lager in die Maschine einzubauen oder aus der Maschine auszubauen. Das Lager stellt ein Verschleißteil der Maschine dar und ein Nachrüsten der Maschine mit der Trennplatte kann somit besonders einfach bei einem routinemäßigen Austausch des Lagers erfolgen. Es ist bevorzugt, dass die Maschine eine Strömungsmaschine ist, insbesondere eine Gasturbine. Es ist weiterhin insbeson¬ dere bevorzugt, dass die Sperrkammer mit der Trennplatte am Turbinenaustritt der Gasturbine angeordnet ist. Es ist vor¬ teilhaft, die Trennplatte hier vorzusehen, weil ein Austreten des Schmierfluids am Turbinenaustritt der Gasturbine beson¬ ders kritisch ist, da es dort in Kontakt mit heißen Abgasen und heißen Teilen der Gasturbine treten und dabei verbrennen kann . The partition plate is preferably fixed by means attached to the bearing end face and on the partition plate spacers. This makes it possible to install the separator plate together with the bearing in the machine or remove it from the machine. The bearing represents a wearing part of the machine and retrofitting the machine with the separating plate can thus be carried out particularly easily during a routine replacement of the bearing. It is preferred that the machine is a turbomachine, in particular a gas turbine. It is further insbeson ¬ particular preferred that the barrier chamber is disposed with the partition plate at the turbine outlet of the gas turbine. It is above ¬ geous to provide the separation plate here because leakage of the lubricating fluid at the turbine outlet of the gas turbine special ¬ is the critical since it occurred there in contact with hot exhaust gases and hot parts of the gas turbine and can burn it.
Das erfindungsgemäße Verfahren zum Betreiben einer Maschine weist die Schritte auf: Rotieren der Welle; Beaufschlagen der Sperrkammer mit Umgebungsluft unter Atmosphärenbedingungen als dem Sperrfluid, wodurch ein Austreten des Schmierfluids aus dem Lager in die Sperrkammer unterbunden wird. Indem Umgebungsluft eingesetzt wird, die insbesondere aus einer The method according to the invention for operating a machine comprises the steps of: rotating the shaft; Inflicting the barrier chamber with ambient air under atmospheric conditions as the barrier fluid, whereby leakage of the lubricating fluid from the bearing is prevented in the barrier chamber. By ambient air is used, in particular from a
Schalleinhausung der Maschine entnommen wird, ist der Wirkungsgrad der Maschine hoch. Durch das Vorsehen des Trennblechs kann ein Austreten des Schmierfluids aus dem Lager in die Sperrkammer unter allen Betriebsbedingungen unterbunden werden . Sound insulation of the machine is taken, the efficiency of the machine is high. By providing the separating plate, leakage of the lubricating fluid from the bearing into the barrier chamber under all operating conditions can be prevented.
Im Folgenden wird anhand der beigefügten schematischen Zeichnungen die Erfindung näher erläutert. Es zeigen In the following the invention will be explained in more detail with reference to the accompanying schematic drawings. Show it
Figur 1 einen Längsschnitt durch eine Maschine, 1 shows a longitudinal section through a machine,
Figur 2 eine Detailansicht des Längsschnitts aus Figur 1 und Figure 2 is a detail view of the longitudinal section of Figure 1 and
Figur 3 die Strömungsverhältnisse in einer Sperrkammer der Figure 3 shows the flow conditions in a barrier chamber of
Maschine .  Machine.
Wie es aus Figuren 1 bis 3 ersichtlich ist, weist eine Ma¬ schine 1 eine Welle 2 auf, die um eine Wellenachse 8 rotier¬ bar ist. Weiterhin weist die Welle 2 eine Stufe 3 auf, wo¬ durch die Welle 2 in Axialrichtung einen ersten Wellenab- schnitt 9 mit einem ersten Radius 11 und einen zweiten Wel¬ lenabschnitt 10 mit einem zweiten Radius 12 aufweist. Der zweite Radius 12 ist dabei kürzer als der erste Radius 11. Durch die Stufe 3 weist die Welle 2 eine rotierbare Wellen- Stirnfläche 6 auf, die in der Grenzfläche zwischen dem ersten Wellenabschnitt 10 und zweiten Wellenabschnitt 11 angeordnet ist und sich radial zwischen dem ersten Radius 11 und dem zweiten Radius 12 erstreckt. Die Wellenstirnfläche 6 ist da¬ durch kreisringförmig. As is apparent from Figures 1 to 3, 1 has an Ma ¬ machine on a shaft 2 which is rotier ¬ about a shaft axis 8 bar. Furthermore, the shaft 2 has a step 3, where ¬ through the shaft 2 in the axial direction, a first Wellenab- section 9 having a first radius 11 and a second Wel ¬ lenabschnitt 10 having a second radius 12. The second radius 12 is shorter than the first radius 11. Through the stage 3, the shaft 2 has a rotatable shaft end face 6, which is arranged in the interface between the first shaft portion 10 and second shaft portion 11 and radially between the first Radius 11 and the second radius 12 extends. The shaft end face 6 is there ¬ by annular.
Die Maschine 1 weist weiterhin ein feststehendes Gehäuse 5 und ein Lager 4 auf, das die Welle 2 an ihrem zweiten Wellenabschnitt 10 an dem Gehäuse 5 abstützt. Das Lager 4 ist mit einem Schmierfluid, insbesondere Öl, geschmiert und ist ins- besondere ein Gleitlager. Das Lager 4 weist eine feststehende Lagerstirnseite 7 auf, die parallel zu der Wellenstirnfläche 6 und der Wellenstirnfläche 6 zugewandt angeordnet ist. Radi¬ al außerhalb der Lagerstirnseite 7 ist eine feststehende Gehäusestirnseite 30 angeordnet, die ebenfalls der Wellen- Stirnfläche 6 zugewandt angeordnet ist. The machine 1 further comprises a fixed housing 5 and a bearing 4, which supports the shaft 2 at its second shaft portion 10 on the housing 5. The bearing 4 is lubricated with a lubricating fluid, in particular oil, and is in particular a slide bearing. The bearing 4 has a fixed bearing end face 7, which is arranged parallel to the shaft end face 6 and the shaft end face 6 facing. Rad ¬ al outside the bearing end face 7, a fixed housing end face 30 is arranged, which is also arranged facing the shaft end face 6.
Die Maschine 1 weist eine Sperrkammer 13 auf, die im Betrieb der Maschine 1 mit einem Sperrfluid beaufschlagt wird, um ein Austreten des Schmierfluids aus dem Lager 4 in die Sperrkam- mer 13 zu unterbinden. Die Sperrkammer 13 ist axial begrenzt von der Wellenstirnfläche 6 und der Lagerstirnseite 7. Radial innen ist die Sperrkammer 13 begrenzt von der Radialaußenseite des sich von der Wellenstirnfläche 6 bis zu der Lager¬ stirnseite 7 erstreckenden Abschnitts des zweiten Wellenab- Schnitts 10. The machine 1 has a blocking chamber 13, which is acted upon by a blocking fluid during operation of the machine 1 in order to prevent leakage of the lubricating fluid from the bearing 4 into the blocking chamber 13. The locking chamber 13 is axially bounded by the shaft end face 6 and the bearing end side 7. Radially inside the locking chamber 13 is bounded by the radial outside of the shaft end face 6 to the bearing ¬ end face 7 extending portion of the second Wellenab- section 10th
Das Lager 4 weist eine Lagerdichtung 14 zum Abdichten des Lagers 4 zur Sperrkammer 13 hin auf. Die Lagerdichtung 14 ist auf der Radialaußenseite der Welle 2 im Bereich des zweiten Wellenabschnitts 10 und im Bereich der Lagerstirnseite 7 an¬ geordnet. Um ein Austreten des Schmierfluids aus dem Lager 4 zu vermeiden, ist es erforderlich, dass der Druck des Sperr- fluids an dem der Sperrkammer 13 zugewandten Ende der Lager- dichtung 14 höher ist als der Druck des Schmiertluids an die¬ sem Ende . The bearing 4 has a bearing seal 14 for sealing the bearing 4 to the locking chamber 13 out. The bearing seal 14 is arranged on the radial outer side of the shaft 2 in the region of the second shaft section 10 and in the region of the bearing end face 7 on ¬ . In order to prevent leakage of the lubricating fluid from the bearing 4, it is necessary for the pressure of the blocking fluid to be at the end of the bearing chamber facing the blocking chamber 13. Seal 14 is higher than the pressure of the lubricating fluid at this ¬ sem end.
In die Sperrkammer 13 ist eine feststehende und sich radial erstreckende Trennplatte 15 eingebracht. Die Trennplatte 15 kann beispielsweise ein Blech sein. Die Trennplatte 15 ist mit ihrer langen Seite parallel zu der Wellenstirnfläche 6 und der Lagerstirnseite 7 angeordnet und kreisringförmig aus¬ gebildet. Durch das Einbringen der Trennplatte 15 in die Sperrkammer 13 werden eine Rotor-Stator-Kammer 27, die sich von der Wellenstirnfläche 6 bis zur Trennplatte 15 erstreckt, und eine Stator-Stator-Kammer 28 ausgebildet, die sich von der Trennplatte 15 bis zur Lagerstirnseite 7 erstreckt. Die Rotor-Stator-Kammer 27 und die Stator-Stator-Kammer 28 sind in Axialrichtung nebeneinander angeordnet. In the barrier chamber 13 is a fixed and radially extending partition plate 15 is introduced. The partition plate 15 may be a sheet, for example. The partition plate 15 is arranged with its long side parallel to the shaft end face 6 and the bearing end face 7 and formed from annular ¬ . By inserting the partition plate 15 in the lock chamber 13, a rotor-stator chamber 27 extending from the shaft end face 6 to the partition plate 15 and a stator-stator chamber 28 are formed extending from the partition plate 15 to the bearing end face 7 extends. The rotor-stator chamber 27 and the stator-stator chamber 28 are arranged side by side in the axial direction.
Zwischen dem radial innen liegenden Längsende der Trennplatte 15 und der Radialaußenseite des zweiten Wellenabschnitts 10 ist ein Radialspalt 16 ausgebildet, der in Radialrichtung ei- ne Erstreckung von 0,1 mm bis 10 mm hat. Die Trennplatte 15 hat einen Abstand von der Wellenstirnfläche 6, der von 0,25*d bis 0,75*d beträgt, wobei d der Abstand zwischen der Wellen¬ stirnfläche 6 und der Lagerstirnseite 7 ist. Radial nach au¬ ßen erstreckt sich die Trennplatte 15 gemäß Figuren 1 bis 3 im Wesentlichen bis zu dem ersten Radius 11. Es ist jedoch denkbar, die Trennplatte 15 auch weiter nach radial außen aus zuführen . Between the radially inner longitudinal end of the partition plate 15 and the radial outer side of the second shaft portion 10, a radial gap 16 is formed, which has an extension of 0.1 mm to 10 mm in the radial direction. The partition plate 15 has a distance from the shaft end face 6, which is from 0.25 * d to 0.75 * d, where d is the distance between the shaft end surface ¬ 6 and the bearing end face 7. Radially outward ¬ SEN, the partition plate 15 extends in accordance with Figures 1 to 3 substantially to the first radius 11. However, it is conceivable to also continue the separator plate 15 radially outward from.
Die Sperrkammer 13 weist eine erste Aussparung 25 auf, die in die Welle 2 eingebracht ist und sich radial außen an den ers¬ ten Radius 11 anschließt. Durch die erste Aussparung 25 ist eine Aussparungsstirnfläche 29 ausgebildet, die der Lager¬ stirnseite 7 zugewandt angeordnet ist. Die Sperrkammer 15 weist weiterhin eine zweite Aussparung 26 auf, die sich nach radial außen erstreckt. Das Sperrfluid mit atmosphärischem Druck kann aus der Umgebung 23 der Maschine 1 in die Sperrkammer 13 via eine durchströmbaren Passage gelangen. Im dargestellten Ausführungsbeispiel umfasst die Passage einen Au- ßenspalt 22, einen Kanal 24 und die zweite Aussparung 26 so¬ wie nicht weitere dargestellte Kanäle, wodurch die Sperrkam¬ mer 13 mit der Umgebung in Strömungsverbindung steht. Ein Turbinenspalt 20 erstreckt sich von der Sperrkammer 13 bis zu einem Turbineninnenraum. Der Turbinenspalt 20 weist eine Turbinendichtung 21 auf. Damit kein Abgas aus dem Turbineninnenraum via den Turbinenspalt 20 in die Sperrkammer 13 gelangen kann, ist es erforderlich, dass der Druck des Sperrgases in der Sperrkammer 13 höher als der Druck des Abgases ist. The seal chamber 13 has a first recess 25 which is inserted into the shaft 2 and radially outwardly adjoining the ers ¬ th radius. 11 Through the first recess 25 a recess end face 29 is formed, which is arranged facing the bearing ¬ end face 7. The locking chamber 15 also has a second recess 26 which extends radially outward. The barrier fluid at atmospheric pressure can pass from the environment 23 of the machine 1 into the blocking chamber 13 via a passage through which it is possible to flow. In the illustrated embodiment, the passage comprises an Au ßenspalt 22, a channel 24 and the second recess 26 so ¬ as not further illustrated channels, whereby the Sperrkam ¬ mer 13 is in flow communication with the environment. A turbine gap 20 extends from the barrier chamber 13 to a turbine interior. The turbine gap 20 has a turbine seal 21. So that no exhaust gas from the turbine interior via the turbine gap 20 can get into the barrier chamber 13, it is necessary that the pressure of the sealing gas in the barrier chamber 13 is higher than the pressure of the exhaust gas.
Die Maschine 1 weist eine Mehrzahl an Abstandshaltern 17 auf, die jeweils an der Lagerstirnseite 7 und an der Trennplatte 15 angebracht sind, um die Trennplatte 17 zu befestigen. Je¬ der der Abstandshalter 17 ist durch ein jeweiliges Loch in der Trennplatte 15 durchgeführt und weist einen Abstandshal- terkopf auf, mit dem das Axialverschieben der Trennplatte 15 in Richtung zu der Wellenstirnfläche 6 begrenzt ist. Jeder Abstandshalter 17 ist von einer Hülse 19 umhüllt, mit der das Axialverschieben der Trennplatte 15 in Richtung zu der Lager- Stirnseite 7 begrenzt ist. The machine 1 has a plurality of spacers 17, which are respectively attached to the bearing end face 7 and to the partition plate 15 to fix the partition plate 17. Je ¬ of the spacer 17 is performed by a respective hole in the partition plate 15 and has a spacer head, with the axial displacement of the partition plate 15 is limited in the direction of the shaft end face 6. Each spacer 17 is enveloped by a sleeve 19, with which the axial displacement of the partition plate 15 is limited in the direction of the bearing end face 7.
Die sich in der Sperrkammer 13 beim Rotieren der Welle 2 einstellenden Strömungsverhältnisse sind in Figur 3 dargestellt. Beim Rotieren der Welle 2 stellt sich in der Sperrkammer 13 eine Strömung ein, die angetrieben wird, weil an der rotierenden Wellenstirnfläche 6 durch Reibung das Sperrfluid nach radial außen transportiert wird. Aus Kontinuitätsgründen strömt in der Rotor-Stator-Kammer 27 das Sperrfluid an der Trennplatte 15 nach radial innen, so dass sich in der Rotor- Stator-Kammer 27 ein Wirbel ausbildet. In der Stator-Stator- Kammer 28 bildet sich eine Strömung aus, die im Wesentlichen nach radial innen gerichtet ist und durch den Radialspalt 16 in Richtung zu der Rotor-Stator-Kammer 27 gerichtet ist. Damit ist die Stator-Stator-Kammer 28, also der Bereich zwi- sehen der Trennplatte 15 und der Lagerstirnseite 7, im We¬ sentlichen wirbelfrei. In der Stator-Stator-Kammer 28 können sich in Ecken oder an Kanten kleine Wirbel ausbildet, diese kleinen Wirbel können jedoch den Druck in der Stator-Stator-Kammer 27 nicht bestimmen. Damit ist der Druck an der Lagerstirnseite 7 höher als es für eine Sperrkammer ohne Trennplatte der Fall wäre. CFD- Rechnungen für einige ausgewählte Fälle haben ergeben, dass der Druck an der Lagerstirnseite 7 an dem radial innen lie¬ genden Ende der Sperrkammer 13 um 2 mbar bis 3 mbar höher ist als es für die Sperrkammer ohne Trennplatte der Fall wäre. The adjusting in the lock chamber 13 during rotation of the shaft 2 flow conditions are shown in Figure 3. During rotation of the shaft 2, a flow is established in the blocking chamber 13, which is driven because the blocking fluid is transported radially outward on the rotating shaft end face 6 by friction. For reasons of continuity flows in the rotor-stator chamber 27, the barrier fluid to the partition plate 15 radially inward, so that in the rotor-stator chamber 27 forms a vortex. In the stator-stator chamber 28, a flow is formed, which is directed substantially radially inward and is directed through the radial gap 16 in the direction of the rotor-stator chamber 27. Thus, the stator-stator chamber 28, ie the area be- see the partition plate 15 and the bearing face 7, wirbelfrei in ¬ We sentlichen. In the stator-stator chamber 28, small vortices can be formed in corners or at edges, but these small vortices can not determine the pressure in the stator-stator chamber 27. Thus, the pressure at the bearing end face 7 is higher than would be the case for a barrier chamber without partition plate. CFD calculations for some selected cases have shown that the pressure at the bearing end face 7 at the radially inner lie ¬ ing end of the barrier chamber 13 by 2 mbar to 3 mbar higher than it would be the case for the barrier chamber without partition plate.
Auch der Druck an der Wellenstirnfläche 6 ist höher als es für die Sperrkammer ohne Trennplatte der Fall wäre, weil der Wirbel in der Rotor-Stator-Kammer 28 durch die Strömung durch den Radialspalt 16 einen höheren Druck aufgeprägt bekommt. Die CFD-Rechnungen haben ergeben, dass der Druck an der Wellenstirnfläche 6 an dem radial innen liegenden Ende der Also, the pressure on the shaft end face 6 is higher than would be the case for the barrier chamber without partition plate, because the vortex in the rotor-stator chamber 28 gets impressed by the flow through the radial gap 16, a higher pressure. The CFD calculations have shown that the pressure at the shaft end surface 6 at the radially inner end of the
Sperrkammer 13 um 1,5 mbar bis 2,5 mbar höher ist als es für die Sperrkammer ohne Trennplatte der Fall wäre. Es wird in der Sperrkammer 13 auch an der radial außerhalb des ersten Radius 11 angeordneten Aussparungsstirnfläche 29 das Sperrfluid nach radial außen gefördert. Die Trennplatte 15 gemäß Figuren 1 bis 3 erstreckt hier sich zwar nur im Wesentlichen bis zu dem ersten Radius 11, jedoch ist der Be- reich radial außerhalb des Radius 11 unkritisch, weil hier der Abstand zwischen der Aussparungsstirnfläche 29 und der Lagerstirnseite 7 und/oder der Gehäusestirnseite 30 ausrei¬ chend groß ist, dass sich kein radiales Druckgefälle ausbil¬ den kann. Locking chamber 13 by 1.5 mbar to 2.5 mbar higher than it would be the case for the barrier chamber without partition plate. It is in the barrier chamber 13 and at the radially outwardly of the first radius 11 arranged recess end face 29, the barrier fluid conveyed radially outward. Although the partition plate 15 according to FIGS. 1 to 3 extends only substantially up to the first radius 11, the area radially outside the radius 11 is not critical because here the distance between the recess end face 29 and the bearing front side 7 and / or the housing end 30 is suffi ¬ ciently large that no radial pressure gradient ausbil ¬ can.
Obwohl die Erfindung im Detail durch das bevorzugte Ausführungsbeispiel näher illustriert und beschrieben wurde, so ist die Erfindung nicht durch die offenbarten Beispiele einge¬ schränkt und andere Variationen können vom Fachmann hieraus abgeleitet werden, ohne den Schutzumfang der Erfindung zu verlassen . Although the invention in detail by the preferred embodiment has been illustrated and described in detail, the invention is not limited ¬ by the disclosed examples and other variations can be derived therefrom by the skilled artisan without departing from the scope of the invention.

Claims

Patentansprüche claims
1. Maschine mit einer Welle (2), die eine Stufe (3) auf¬ weist, so dass ein erster Wellenabschnitt (9) mit einem ersten Durchmesser (11), ein zweiter Wellenabschnitt (10) mit einem zweiten Durchmesser (12), der kürzer als der erste Durchmesser (11) ist, und eine sich radial erstreckende sowie rotierbare Wellenstirnfläche (6) ausgebildet sind, einem Gehäuse (5) und einem Lager (4), das die Welle (2) an ihrem zweiten Wellenabschnitt (10) an dem Gehäuse (5) ab¬ stützt und mit einem Schmierfluid geschmiert ist, 1. Machine having a shaft (2), which has a step (3) on ¬ , so that a first shaft portion (9) having a first diameter (11), a second shaft portion (10) having a second diameter (12), which is shorter than the first diameter (11), and a radially extending and rotatable shaft end surface (6) are formed, a housing (5) and a bearing (4), the shaft (2) at its second shaft portion (10) on the housing (5) from ¬ supported and lubricated with a lubricating fluid,
wobei die Wellenstirnfläche (6) einer sich radial erstre¬ ckenden sowie feststehenden Lagerstirnseite (7) zugewandt ist, wodurch eine mit einem Sperrfluid, mittels dem ein Austreten des Schmierfluids aus dem Lager (4) unterbindbar ist, beaufschlagbaren Sperrkammer (13) ausgebildet ist, die axial von der Wellenstirnfläche (6) und der Lagerstirnseite (7) sowie radial innen von dem von dem Lager (4) freigelassenen zweiten Wellenabschnitt (10) begrenzt ist, wherein the shaft end surface (6) faces a radially erstre ¬ ckenden and fixed bearing end face (7), whereby one with a barrier fluid, by means of which a leakage of the lubricating fluid from the bearing (4) can be prevented, can be acted upon lock chamber (13) is formed the second shaft section (10), which is axially delimited by the shaft end face (6) and the bearing end face (7) and radially inward by that of the bearing (4), is delimited,
dadurch gekennzeichnet, dass  characterized in that
die Sperrkammer (13) über eine Passage (24, 26) mit der Umgebung verbunden ist und dass in der Sperrkammer eine sich radial erstreckende und feststehende Trennplatte (15) ange¬ ordnet ist, so dass eine aerodynamische Abschirmung der La¬ gerstirnseite (7) von der Wellenstirnfläche (6) erfolgt, wodurch der Bereich zwischen der Trennplatte (15) und der Lagerstirnseite (7) beim Rotieren der Welle (2) im Wesent¬ lichen wirbelfrei ist. the barrier chamber (13) via a passage (24, 26) is connected to the environment and that a radially extending and fixed separating plate in the blocking chamber (15) is ¬ arranged so that an aerodynamic shield of La ¬ gerstirnseite (7) from the shaft end surface (6) takes place, whereby the area between the partition plate (15) and the bearing face (7) during rotation of the shaft (2) in Wesent ¬ union is irrotational.
2. Maschine gemäß Anspruch 1, 2. Machine according to claim 1,
wobei zwischen dem radial innen liegenden Längsende der Trennplatte (15) und der Welle (2) ein Radialspalt (16) ausgebildet ist. wherein between the radially inner longitudinal end of the partition plate (15) and the shaft (2), a radial gap (16) is formed.
3. Maschine gemäß Anspruch 2, 3. Machine according to claim 2,
wobei der Radialspalt (16) eine Erstreckung in Radialrichtung von 0,1 mm bis 10 mm hat.  wherein the radial gap (16) has an extent in the radial direction of 0.1 mm to 10 mm.
4. Maschine gemäß einem der Ansprüche 1 bis 3, 4. Machine according to one of claims 1 to 3,
wobei die Trennplatte (15) parallel zu der Wellenstirnflä¬ che (6) und der Lagerstirnseite (7) angeordnet ist. wherein the partition plate (15) parallel to the Wellenstirnflä ¬ surface (6) and the bearing end face (7) is arranged.
5. Maschine gemäß einem der Ansprüche 1 bis 4, 5. Machine according to one of claims 1 to 4,
wobei die Trennplatte (15) einen Abstand von der Wellen¬ stirnfläche hat, der von 0,25*d bis 0,75*d, bevorzugt von 0,5*d bis 0,75*d, besonders bevorzugt 0,5*d, beträgt, wobei d der Abstand zwischen der Wellenstirnfläche (6) und der Lagerstirnseite (7) ist. wherein the partition plate (15) has a distance from the shaft end face ¬ of 0.25 * d to 0.75 * d, preferably from 0.5 * d to 0.75 * d, more preferably 0.5 * d , is, where d is the distance between the shaft end face (6) and the bearing end face (7).
6. Maschine gemäß einem der Ansprüche 1 bis 5, 6. Machine according to one of claims 1 to 5,
wobei die Trennplatte (15) sich nach radial außen im We- sentlichen bis mindestens zu dem radial außen liegenden Ende der Wellenstirnfläche (6) erstreckt.  wherein the partition plate (15) extends radially outwardly substantially to at least the radially outer end of the shaft end face (6).
7. Maschine gemäß einem der Ansprüche 1 bis 6, 7. Machine according to one of claims 1 to 6,
wobei die Trennplatte (15) kreisringförmig um die Welle (2) herum angeordnet ist.  wherein the partition plate (15) is arranged annularly around the shaft (2).
8. Maschine gemäß einem der Ansprüche 1 bis 7, 8. Machine according to one of claims 1 to 7,
wobei die Trennplatte (15) mittels an der Lagerstirnseite (7) und an der Trennplatte angebrachten Abstandshaltern (17) befestigt ist.  wherein the partition plate (15) is fixed by means of spacers (17) attached to the bearing end face (7) and to the partition plate.
9. Maschine gemäß einem der Ansprüche 1 bis 8, 9. Machine according to one of claims 1 to 8,
wobei die Maschine eine Strömungsmaschine ist, insbesondere eine Gasturbine,  wherein the machine is a turbomachine, in particular a gas turbine,
wobei die Sperrkammer (13) mit der Trennplatte (15) insbe¬ sondere am Turbinenaustritt der Gasturbine angeordnet ist. wherein the barrier chamber (13) with the partition plate (15) in particular ¬ special is arranged at the turbine outlet of the gas turbine.
10. Verfahren zum Betreiben einer Maschine (1) gemäß einem der Ansprüche 1 bis 9 mit den Schritten: 10. A method of operating a machine (1) according to any one of claims 1 to 9, comprising the steps of:
- Rotieren der Welle (2);  - rotating the shaft (2);
- Beaufschlagen der Sperrkammer (13) mit Umgebungsluft un- ter Atmosphärenbedingungen als dem Sperrfluid, wodurch ein - Subjecting the barrier chamber (13) with ambient air under atmospheric conditions as the barrier fluid, whereby a
Austreten des Schmierfluids aus dem Lager (4) in die Sperrkammer (13) unterbunden wird. Leakage of the lubricating fluid from the bearing (4) in the barrier chamber (13) is prevented.
EP15744517.2A 2014-07-30 2015-07-21 Machine with a shaft and a bearing Active EP3129604B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14179077.4A EP2980363A1 (en) 2014-07-30 2014-07-30 Machine and a method for operating the machine
PCT/EP2015/066640 WO2016016048A1 (en) 2014-07-30 2015-07-21 Machine and method for operating the machine

Publications (2)

Publication Number Publication Date
EP3129604A1 true EP3129604A1 (en) 2017-02-15
EP3129604B1 EP3129604B1 (en) 2018-12-05

Family

ID=51260650

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14179077.4A Withdrawn EP2980363A1 (en) 2014-07-30 2014-07-30 Machine and a method for operating the machine
EP15744517.2A Active EP3129604B1 (en) 2014-07-30 2015-07-21 Machine with a shaft and a bearing

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP14179077.4A Withdrawn EP2980363A1 (en) 2014-07-30 2014-07-30 Machine and a method for operating the machine

Country Status (4)

Country Link
US (1) US10570769B2 (en)
EP (2) EP2980363A1 (en)
CN (1) CN106536868B (en)
WO (1) WO2016016048A1 (en)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1045973A (en) * 1962-07-14 1966-10-19 Walter Eberspacher Exhaust turbo supercharger
DE3441351C2 (en) * 1984-11-13 1986-10-02 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Centrifugal mechanical seal
DE4420973A1 (en) * 1994-06-16 1995-12-21 Abb Management Ag Axial gas turbine shaft seal for turbo engine
JP4773804B2 (en) * 2005-11-17 2011-09-14 三菱重工業株式会社 gas turbine
US20120201661A1 (en) * 2011-02-07 2012-08-09 General Electric Company Contaminant shield system for a shaft

Also Published As

Publication number Publication date
US20180209289A1 (en) 2018-07-26
EP2980363A1 (en) 2016-02-03
WO2016016048A1 (en) 2016-02-04
CN106536868B (en) 2018-05-11
US10570769B2 (en) 2020-02-25
EP3129604B1 (en) 2018-12-05
CN106536868A (en) 2017-03-22

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